JP5496982B2 - Gear coupling and manufacturing method thereof - Google Patents
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Description
本発明は、2つの回転軸の軸方向および半径方向の相対変位を許容して、回転軸同士の滑らかな動力伝達を行うギヤカップリングおよびその製造方法に関する。 The present invention relates to a gear coupling that allows a relative displacement in the axial direction and the radial direction of two rotating shafts to perform smooth power transmission between the rotating shafts, and a manufacturing method thereof.
ギヤカップリングは、2つの回転軸にそれぞれ連結されるハブに設けられた外歯車と、スリーブに設けられた内歯車との噛み合いによって、回転軸の軸方向および半径方向の相対変位を許容して、正しく動力を伝達することを可能にしている。このとき、外歯車と内歯車は、それぞれ相対変位によって生じる傾斜角をもって噛み合い、相対変位が変化すると傾斜角も変化する。 The gear coupling allows relative displacement in the axial direction and the radial direction of the rotary shaft by meshing between an external gear provided on the hub connected to each of the two rotary shafts and an internal gear provided on the sleeve. It is possible to transmit power correctly. At this time, the external gear and the internal gear mesh with each other with an inclination angle caused by relative displacement, and the inclination angle changes when the relative displacement changes.
このように外歯車と内歯車が種々の傾斜角の下で噛み合うためには、両歯車あるいはどちらか片方の歯車の歯面に円弧状の膨らみを与える必要がある。この歯面に膨らみを与えることをクラウニングといい、一般には図19に示すように外歯車に対して与える。クラウニングは、非特許文献1に記載のようにギヤカップリングの性能を左右する最も重要な設計因子であり、許容する傾斜角や伝達動力を考慮して決定する必要がある。従来、用いる歯車をインボリュート歯車とすることを前提に、いくつかのクラウニング法が提案されている。 Thus, in order for the external gear and the internal gear to mesh with each other at various inclination angles, it is necessary to give an arcuate bulge to the tooth surfaces of both gears or one of the gears. Giving the tooth surface bulge is called crowning and is generally given to the external gear as shown in FIG. Crowning is the most important design factor that affects the performance of the gear coupling as described in Non-Patent Document 1, and must be determined in consideration of the allowable inclination angle and transmission power. Conventionally, several crowning methods have been proposed on the assumption that the gear to be used is an involute gear.
例えば、特許文献1には、2つの回転軸に連結される外歯車のピッチ円近傍の歯面を、歯幅中央においては歯丈方向、最大許容傾斜角においては歯幅端近くで接触する歯面とし、指数関数曲線に沿って外歯車にクラウニングを与えることが記載されている。また、特許文献2には、複数の円弧からなる外歯車のピッチ円上の歯すじ曲線を構成する歯幅中央の円弧R1と、この歯幅中央の円弧R1に連続する円弧R2との変曲点を歯幅中央寄りにして、円弧R1が歯幅に対して占める割合を減少させた外歯車とするクラウニングが記載されている。 For example, in Patent Document 1, a tooth surface in the vicinity of a pitch circle of an external gear connected to two rotation shafts is in contact with the tooth width direction at the center of the tooth width and near the tooth width end at the maximum allowable inclination angle. It is described that the external gear is crowned along the exponential curve. Further, Patent Document 2 discloses an inflection between an arc R1 at the center of the tooth width constituting a tooth curve on the pitch circle of the external gear composed of a plurality of arcs and an arc R2 continuous to the arc R1 at the center of the tooth width. A crowning is described in which the point is closer to the center of the tooth width and the external gear has a reduced ratio of the arc R1 to the tooth width.
しかしながら、ギヤカップリングにおける歯面のクラウニングは、その付加量が極めて大きいこともあって、その加工はホブ盤等による創成加工で行う場合がほとんどである。このため、非特許文献2にも記載のように、加工したクラウニング歯面が歯車の歯幅中央に関して非対称となり、ギヤカップリングにおける振動騒音の原因となるという問題を抱えている。 However, the crowning of the tooth surface in the gear coupling is very large, and the machining is almost always performed by generating work using a hobbing machine or the like. For this reason, as described in Non-Patent Document 2, there is a problem that the processed crowning tooth surface is asymmetric with respect to the center of the gear width of the gear and causes vibration noise in the gear coupling.
そこで、本発明においては、大きな相対変位を許容しつつ、大きな伝達動力と小さな振動騒音を実現する安価なギヤカップリングおよびその製造方法を提供することを目的とする。 Accordingly, an object of the present invention is to provide an inexpensive gear coupling that realizes a large transmission power and a small vibration noise while allowing a large relative displacement, and a manufacturing method thereof.
上記課題を解決するため、本発明のギヤカップリングは、2つの外歯車と、2つの外歯車に噛み合う内歯車とから構成されるギヤカップリングにおいて、外歯車および内歯車の基準断面歯形が、外歯車および内歯車の歯数よりも多い歯数のインボリュート歯車の歯形であることを特徴とする。従来ギヤカップリングに用いる外歯車および内歯車の基準断面歯形は、外歯車および内歯車の歯数と同じ歯数のインボリュート歯形とするのが常識であり、通常の歯車の場合、異なる歯数のインボリュート歯形を採用することは理論的にあり得ない。本発明のギヤカップリングでは、外歯車および内歯車の歯数よりも多い歯数のインボリュート歯車の歯形を採用する。 In order to solve the above-described problem, the gear coupling of the present invention is a gear coupling including two external gears and an internal gear meshing with the two external gears. The tooth profile of the involute gear is greater than the number of teeth of the external gear and the internal gear. Conventionally, the standard cross-sectional tooth profile of the external gear and internal gear used for gear coupling is an involute tooth profile having the same number of teeth as that of the external gear and internal gear. It is theoretically impossible to adopt an involute tooth profile. In the gear coupling of the present invention, a tooth profile of an involute gear having a larger number of teeth than that of the external gear and the internal gear is employed.
これにより、従来設定した相対変位(傾斜角)でしか良くならなかった歯当たりが、本発明のギヤカップリングではあらゆる傾斜角において実現することが可能となる。なお、外歯車および内歯車の歯数よりも多い歯数のインボリュート歯車の歯形とは、誤差以上の形状の相違が得られる歯数のインボリュート歯車の歯形をいう。 As a result, the tooth contact that has been improved only by the relative displacement (tilt angle) set in the past can be realized at any tilt angle in the gear coupling of the present invention. Note that the tooth profile of the involute gear having the number of teeth larger than the number of teeth of the external gear and the internal gear refers to the tooth profile of the involute gear having the number of teeth from which a difference in shape exceeding the error can be obtained.
ここで、外歯車および内歯車の歯数を無限大とした場合には、外歯車および内歯車の基準断面歯形は台形となる。従来ギヤカップリングに用いる歯車の歯形は、インボリュート歯形とするのが常識とされているが、本発明のギヤカップリングでは、通常の歯車では決して噛み合うことのない台形歯形を採用している。 Here, when the number of teeth of the external gear and the internal gear is infinite, the reference cross-sectional tooth profile of the external gear and the internal gear is a trapezoid. Conventionally, it is common knowledge that the gear tooth profile used for gear coupling is an involute tooth profile, but the gear coupling of the present invention employs a trapezoidal tooth profile that never meshes with a normal gear.
従来、ギヤカップリングの外歯車は、ホブ盤による創成加工によってクラウニングが与えられてきた。しかし、この場合の外歯車は、歯面が歯幅中央に関して非対称となり、振動発生の原因となっている。そこで、本発明では、基準断面歯形を外歯車および内歯車の歯数よりも多い歯数のインボリュート歯車の歯形とする外歯車および内歯車の歯面を、成形加工法により形成することにより、歯幅中央に関して対称なクラウニング歯面を形成する。 Conventionally, an external gear of a gear coupling has been given crowning by a creation process using a hobbing machine. However, in this case, the tooth surface of the external gear becomes asymmetric with respect to the center of the tooth width, causing vibration. Therefore, in the present invention, the tooth surfaces of the external gear and the internal gear whose reference cross-sectional tooth profile is the tooth profile of the involute gear having a larger number of teeth than the external gear and the internal gear are formed by a molding method. A symmetrical tooth surface is formed with respect to the center of the width.
また、本発明のギヤカップリングでは、外歯車には成形加工法によりクラウニング歯面を形成するので、従来のホブ盤による創成加工と異なり、歯車材に対する工具の切り込みが歯幅中央に関して対称となり、歯幅中央に関して対称なクラウニング歯面が形成される。 In addition, in the gear coupling of the present invention, the outer gear is formed with a crowning tooth surface by a molding method, so unlike the conventional hobbing process, the cutting of the tool with respect to the gear material is symmetric with respect to the center of the tooth width, A crowning tooth surface symmetrical with respect to the center of the tooth width is formed.
(1)外歯車および内歯車の基準断面歯形が、外歯車および内歯車の歯数よりも多い歯数のインボリュート歯車の歯形であることにより、相対変位の大小に拘わらず、理想的な歯当たりを実現することが可能となり、大きな相対変位を許容しつつ、大きな伝達動力と小さな振動騒音を実現することができる。 (1) Since the reference cross-sectional tooth profile of the external gear and the internal gear is the tooth profile of the involute gear having a larger number of teeth than the external gear and the internal gear, the ideal tooth contact regardless of the relative displacement. It is possible to realize a large transmission power and a small vibration noise while allowing a large relative displacement.
(2)特に、外歯車および内歯車の基準断面歯形を、歯数が無限大の場合の歯形である台形とすることにより、歯車の加工に用いる工具形状も台形となる。このため、工具の製作が容易となり、加工精度および加工能率の向上に繋がる。特に、ギヤカップリングの伝達動力を増加させる目的で、外歯車および内歯車に焼き入れ処理を施す場合は、歯車を研削によって仕上げる必要があるが、本発明のギヤカップリングでは、基準断面歯形を台形としているため、砥石の形状も台形となる。このため、砥石の整形が容易となり、歯車の加工精度および加工能率が向上し、ギヤカップリングの性能向上およびコスト低減に繋がる。 (2) In particular, when the reference cross-sectional tooth profile of the external gear and the internal gear is a trapezoid that is a tooth profile when the number of teeth is infinite, the tool shape used for gear processing also becomes a trapezoid. For this reason, manufacture of a tool becomes easy and it leads to improvement of processing accuracy and processing efficiency. In particular, when the external gear and the internal gear are subjected to a quenching process for the purpose of increasing the transmission power of the gear coupling, it is necessary to finish the gear by grinding. However, in the gear coupling of the present invention, the reference cross-sectional tooth profile is set. Since it is trapezoidal, the shape of the grindstone is also trapezoidal. For this reason, shaping of a grindstone becomes easy, the processing accuracy and processing efficiency of a gear improve, and it leads to the performance improvement and cost reduction of a gear coupling.
(3)基準断面歯形を外歯車および内歯車の歯数よりも多い歯数のインボリュート歯車とし、成形加工法で加工した外歯車のクラウニング歯面は、基準断面歯形をインボリュート歯形とした場合と比較して、歯幅端断面における歯形圧力角の変化が小さく、歯の接触を歯丈方向に広げる効果がある。このため、異常摩耗や焼き付きが生じにくく、面圧強度やスコーリング強度(耐焼き付き性能)が向上し、伝達動力が増加する。また、成形加工法によって加工したクラウニング歯面は、創成運動を与えていないため、歯車の歯元に切り下げ(アンダーカット)が発生せず、歯の曲げ強度が増加し、伝達動力の増大に繋がる。 (3) The reference tooth profile is an involute gear with more teeth than the external gear and the internal gear, and the crowning tooth surface of the external gear machined by the forming method is compared with the reference profile tooth profile being an involute tooth profile. Thus, the change in the tooth profile pressure angle in the tooth width end cross section is small, and there is an effect of expanding the tooth contact in the tooth height direction. For this reason, abnormal wear and seizure hardly occur, the surface pressure strength and scoring strength (seizure resistance performance) are improved, and the transmission power is increased. In addition, since the crowning tooth surface processed by the molding method does not give a creation motion, the gear tooth base does not cut down (undercut), the tooth bending strength increases, and the transmission power increases. .
(4)本発明のギヤカップリングでは、外歯車に歯幅中央に関して対称なクラウニング歯面が形成されているので、ギヤカップリングの外周上における対角位置の2箇所で均等な接触が生じるようになり、振動騒音の低減に繋がる。 (4) In the gear coupling according to the present invention, the outer gear is formed with a crowning tooth surface symmetrical with respect to the center of the tooth width, so that uniform contact occurs at two diagonal positions on the outer periphery of the gear coupling. This leads to reduction of vibration noise.
図1は本発明の実施の形態におけるギヤカップリングの断面図、図2は図1のギヤカップリングの回転軸の変位状態を示す断面図、図3は図1のギヤカップリングの外歯車および内歯車の基準断面歯形形状を示す図である。 1 is a sectional view of a gear coupling according to an embodiment of the present invention, FIG. 2 is a sectional view showing a displacement state of a rotation shaft of the gear coupling of FIG. 1, and FIG. 3 is an external gear of the gear coupling of FIG. It is a figure which shows the reference | standard cross-section tooth profile shape of an internal gear.
図1において、本発明の実施の形態におけるギヤカップリング1は、回転軸1a,1bにそれぞれ連結されるハブ2a,2bと、ハブ2a,2bがそれぞれ収容されるスリーブ3a,3bとを備える。ハブ2a,2bには、それぞれ一様なR曲面のクラウニングが施された外歯車4a,4bが形成されている。一方、スリーブ3a,3bには、それぞれハブ2a,2bの外歯車4a,4bに噛み合う内歯車5a,5bが形成されている。 Referring to FIG. 1, a gear coupling 1 according to an embodiment of the present invention includes hubs 2a and 2b connected to rotating shafts 1a and 1b, and sleeves 3a and 3b in which the hubs 2a and 2b are respectively housed. The hubs 2a and 2b are formed with external gears 4a and 4b, respectively, on which uniform R curved crowning is applied. On the other hand, the sleeves 3a and 3b are formed with internal gears 5a and 5b that mesh with the external gears 4a and 4b of the hubs 2a and 2b, respectively.
なお、本実施形態におけるギヤカップリング1は、鉄道車両の原動機(電動機)の回転軸(原動軸)と、台車の車軸に組み込まれた歯車装置の回転軸(駆動軸)とを揺動自在に接続するものであり、図2に示すように回転軸1a,1bの軸方向および半径方向の相対変位を許容して、回転軸1a,1b同士の動力伝達を行うものである。ギヤカップリング1の回転軸1a,1bのいずれか一方は、原動機の回転軸に連結され、他の一方は、台車の車軸に組み込まれた歯車装置に連結される。 Note that the gear coupling 1 in the present embodiment is capable of swinging between a rotating shaft (driving shaft) of a prime mover (electric motor) of a railway vehicle and a rotating shaft (driving shaft) of a gear device incorporated in the axle of the carriage. As shown in FIG. 2, the power transmission between the rotary shafts 1a and 1b is performed while allowing relative displacement in the axial direction and the radial direction of the rotary shafts 1a and 1b. One of the rotation shafts 1a and 1b of the gear coupling 1 is connected to the rotation shaft of the prime mover, and the other one is connected to a gear device incorporated in the axle of the carriage.
ここで、ハブ2a,2bの外歯車4a,4bおよびスリーブ3a,3bの内歯車5a,5bの基準断面歯形は、外歯車4a,4bおよび内歯車5a,5bの歯数(以下、「製品諸元歯数N0」と称す。)よりも多い歯数(以下、「歯形歯数N」と称す。)のインボリュート歯車の歯形(図3参照。)を採用する。なお、歯形歯数Nは、誤差以上の形状が得られる歯数、例えば、製品諸元歯数N0よりも25%以上多い歯数、すなわち、外歯車4a,4bおよび内歯車5a,5bの製品諸元歯数N0が40の場合、この歯数よりも25%以上多い歯数N=50以上のインボリュート歯車の歯形を採用する。 Here, the reference cross-sectional tooth profile of the external gears 4a and 4b of the hubs 2a and 2b and the internal gears 5a and 5b of the sleeves 3a and 3b is the number of teeth of the external gears 4a and 4b and the internal gears 5a and 5b (hereinafter referred to as “product various types”). An involute gear tooth profile (refer to FIG. 3) having a larger number of teeth (hereinafter referred to as “tooth profile tooth number N”) than the original tooth number N 0 is adopted. Incidentally, tooth number of teeth N is the number of teeth error or more shapes can be obtained, for example, many teeth over 25% than the product specifications teeth N 0, i.e., the external gear 4a, 4b and the internal gear 5a, 5b of the If the product specifications tooth number N 0 is 40, employing a tooth profile of the teeth number N = 50 or more involute gear often 25% or more than the number of teeth.
図3に示すように、ハブ2a,2bの外歯車4a,4bおよびスリーブ3a,3bの内歯車5a,5bの基準断面歯形は、それぞれ製品諸元歯数よりも多い歯数のインボリュート形状に形成されている。各歯はそれぞれの歯厚の中心線Cに対して左右対称となっている。なお、内歯車5a,5bおよび外歯車4a,4bの歯形の形成は、成形加工法による。また、ハブ2a,2bの外歯車4a,4bの歯先と歯元角部における片当たりを避けるため、外歯車4a,4bに適切な歯形修整を与える場合もある。 As shown in FIG. 3, the reference cross-sectional tooth shapes of the external gears 4a and 4b of the hubs 2a and 2b and the internal gears 5a and 5b of the sleeves 3a and 3b are each formed in an involute shape having a greater number of teeth than the number of product specifications. Has been. Each tooth is symmetric with respect to the center line C of each tooth thickness. Note that the tooth shapes of the internal gears 5a and 5b and the external gears 4a and 4b are formed by a molding method. In addition, in order to avoid contact between the tooth tips and the root portion of the external gears 4a and 4b of the hubs 2a and 2b, an appropriate tooth profile modification may be given to the external gears 4a and 4b.
このような本実施形態におけるギヤカップリング1では、歯幅中央に対して対称なクラウニング歯面をもつ外歯車4a,4bと内歯車5a,5bは、図5に示すように傾斜角によって外周上の2箇所P,Qで幾何学的な接触を行う。このギヤカップリング1は、基準断面歯形が製品諸元歯数よりも多い歯数のインボリュート形状であるため、クラウニングによる歯幅端歯形の圧力角の変化が小さく、歯丈方向の歯当たりが確保され易いことから、異常摩耗や焼き付きが生じにくく、面圧強度やスコーリング強度(耐焼き付き性能)が向上し、伝達動力が増加する。 In the gear coupling 1 according to the present embodiment, the external gears 4a and 4b and the internal gears 5a and 5b having the crowning tooth surfaces symmetrical with respect to the center of the tooth width are arranged on the outer periphery by an inclination angle as shown in FIG. Geometrical contact is made at two locations P and Q. This gear coupling 1 has an involute shape with a reference cross-section tooth profile that is greater than the number of product specifications, so the change in the pressure angle of the tooth width end profile due to crowning is small, and the tooth contact in the tooth height direction is secured. Therefore, abnormal wear and seizure hardly occur, surface pressure strength and scoring strength (seizure resistance performance) are improved, and transmission power is increased.
一方、従来のギヤカップリングのように外歯車の歯面が非対称の場合は、図6に示すように外周上の1箇所(接触点S1)でしか接触しない。また、この場合、伝達トルクが作用すると、外歯車と内歯車の間に芯ずれが発生し、外歯車の歯先と内歯車の歯底とが接触し(図6の接触点S2)、結果として、両歯車は約90度離れた外周上の2箇所(接触点S1,S2)で接触する。このような接触は、伝達トルクが一定のとき、支点間距離を減少させ、結果として、歯面が対称の場合に比べて接触荷重が大きくなり、回転するギヤカップリングの面圧強度およびスコーリング強度の低下と振動騒音増加の原因となる。 On the other hand, when the tooth surface of the external gear is asymmetric as in the conventional gear coupling, the contact is made only at one place (contact point S 1 ) on the outer periphery as shown in FIG. Further, in this case, when the transmission torque acts, a misalignment occurs between the external gear and the internal gear, the tooth tip of the external gear contacts the tooth bottom of the internal gear (contact point S 2 in FIG. 6), As a result, the two gears come into contact at two locations (contact points S 1 and S 2 ) on the outer circumference that are approximately 90 degrees apart. Such contact reduces the distance between the fulcrums when the transmission torque is constant. As a result, the contact load becomes larger than when the tooth surfaces are symmetrical, and the surface pressure strength and scoring of the rotating gear coupling are increased. This causes a decrease in strength and an increase in vibration noise.
このように、ギヤカップリングの振動騒音を減少させるためには、本実施形態におけるギヤカップリング1のような対称のクラウニングが不可欠である。特に、本実施形態におけるギヤカップリング1では、外歯車および内歯車の歯形が製品諸元歯数よりも多い歯数の対称なインボリュート形状であることで、回転時の芯ずれの発生が防止され、芯ずれ発生による振動を排除することができるので、低騒音のギヤカップリングを実現できる。 Thus, in order to reduce the vibration noise of the gear coupling, symmetrical crowning like the gear coupling 1 in this embodiment is indispensable. In particular, in the gear coupling 1 according to the present embodiment, the tooth shapes of the external gear and the internal gear are symmetrical involute shapes having a greater number of teeth than the product specifications, thereby preventing misalignment during rotation. Since vibration due to the occurrence of misalignment can be eliminated, a low noise gear coupling can be realized.
なお、歯形歯数についてはN=∞を採用することも可能である。この場合、外歯車および内歯車の基準断面歯形は台形となり、図4に示すように、ハブ12a,12bの外歯車14a,14bおよびスリーブ13a,13bの内歯車15a,15bの基準断面歯形は、それぞれ台形に形成される。各歯はそれぞれの歯厚の中心線Cに対して左右対称となっている。なお、内歯車15a,15bおよび外歯車14a,14bの歯形の形成は、成形加工法による。また、ハブ12a,12bの外歯車14a,14bの歯先と歯元角部における片当たりを避けるため、外歯車14a,14bに適切な歯形修整を与える場合もある。 Note that N = ∞ can be adopted for the number of teeth. In this case, the reference cross-section tooth profile of the external gear and the internal gear is trapezoidal, and as shown in FIG. 4, the reference cross-section tooth profiles of the external gears 14a and 14b of the hubs 12a and 12b and the internal gears 15a and 15b of the sleeves 13a and 13b are Each is formed into a trapezoid. Each tooth is symmetric with respect to the center line C of each tooth thickness. The tooth shapes of the internal gears 15a and 15b and the external gears 14a and 14b are formed by a molding method. In addition, in order to avoid contact with the tooth tips and tooth roots of the external gears 14a and 14b of the hubs 12a and 12b, an appropriate tooth profile modification may be given to the external gears 14a and 14b.
このような基準断面歯形が台形であるギヤカップリング11においても、歯幅中央に対して対称なクラウニング歯面をもつ外歯車14a,14bと内歯車15a,15bは、図5に示したように傾斜角によって外周上の2箇所P,Qで幾何学的な接触を行う。このギヤカップリング11においても、クラウニングによる歯幅端歯形の圧力角の変化が小さく、歯丈方向の歯当たりが確保され易いことから、異常摩耗や焼き付きが生じにくく、面圧強度やスコーリング強度(耐焼き付き性能)が向上し、伝達動力が増加する。 Also in the gear coupling 11 having the trapezoidal reference cross-section tooth profile, the external gears 14a and 14b and the internal gears 15a and 15b having crowning tooth surfaces symmetrical to the center of the tooth width are as shown in FIG. Geometrical contact is made at two points P and Q on the outer periphery according to the inclination angle. Also in this gear coupling 11, since the change in the pressure angle of the tooth width end tooth profile due to crowning is small and the tooth contact in the tooth height direction is easily secured, abnormal wear and seizure hardly occur, and the surface pressure strength and scoring strength. (Seizure-proof performance) is improved and transmission power is increased.
また、このギヤカップリング11は、歯形が直線的な形状である台形であり、加工性が良いため、低コストで製造することが可能である。さらに、歯形が直線的な形状であるため、測定精度が向上する。また、このギヤカップリング11においても回転時の芯ずれの発生が防止されており、芯ずれ発生による振動を排除することができるので、低騒音のギヤカップリングを実現可能である。 Further, the gear coupling 11 is a trapezoid whose tooth shape is a linear shape, and has good workability, so that it can be manufactured at a low cost. Furthermore, since the tooth profile is a linear shape, the measurement accuracy is improved. In addition, the gear coupling 11 also prevents the occurrence of misalignment during rotation, and the vibration caused by the misalignment can be eliminated, so that a low noise gear coupling can be realized.
本実施例では、コンピュータ上に座標点で表した工具を三次元的に作成し、工具に実際の成形加工と同じ動きを与えて、被加工物(上記実施形態におけるギヤカップリング1)の歯面形状を計算し、計算した歯面形状に基づきギヤカップリングの噛み合い状態のシミュレーションを行った。シミュレーションにおいては、理論値による歯面形状ではなく、実際に加工される歯面形状を用いているため、実際のギヤカップリングにおける噛み合い状態を正確に解明することを可能としている。 In the present embodiment, a tool represented by coordinate points is three-dimensionally created on a computer, and the tool is given the same movement as the actual forming process, so that the teeth of the workpiece (gear coupling 1 in the above embodiment) are processed. The surface shape was calculated, and the meshing state of the gear coupling was simulated based on the calculated tooth surface shape. In the simulation, since the tooth surface shape that is actually processed is used instead of the tooth surface shape according to the theoretical value, the meshing state in the actual gear coupling can be accurately clarified.
ギヤカップリングの噛み合い状態について説明する。ギヤカップリングの入力軸と出力軸の関係は、最終的には図7(a)に示すような一組のハブとスリーブの傾斜角δとして表される。このとき、無負荷であれば、噛み合う歯数は同図(b)に示すように傾斜角δが最大となる回転角θ=90°と270°付近の2枚だけとなるが、実際には歯のたわみや加工誤差など様々な要因によって、噛み合い歯数は増減することとなる。本実施例においては、歯面に掛かる荷重による撓み量を10μm程度として考えることとし、最小隙間が10μm以下の歯を噛み合い歯数とした。 The meshing state of the gear coupling will be described. The relationship between the input shaft and the output shaft of the gear coupling is finally expressed as an inclination angle δ of a pair of hub and sleeve as shown in FIG. At this time, if there is no load, the number of teeth engaged is only two rotation angles θ = 90 ° and around 270 ° at which the inclination angle δ is maximum as shown in FIG. The number of meshing teeth increases or decreases due to various factors such as tooth deflection and processing errors. In this embodiment, the amount of deflection due to the load applied to the tooth surface is considered to be about 10 μm, and the teeth having a minimum gap of 10 μm or less are set as the number of meshing teeth.
図8は、従来のホブ盤で歯切りした外歯車と内歯車の噛み合いシミュレーションを行った結果のδ=5°の場合の傾斜角による最小歯面隙間の変化を示している。θ=90°と270°付近で最小隙間が極小値をとるが、歯面が歯幅中央に関して非対称であるため、2箇所の極小値間に約50μmの差eが生じ、芯ずれが発生する可能性がある。この芯ずれは、外歯車の歯先と内歯車の歯底の接触を誘発し(図6の接触点S2)、結果として、両歯車は約90度離れた外周上の2箇所で接触する。このような接触は、伝達トルクが一定のとき、支点間距離を減少させ、結果として、歯面が対称の場合に比べて接触荷重が大きくなり、回転するギヤカップリングの面圧強度およびスコーリング強度の低下と振動騒音増加の原因となる。 FIG. 8 shows a change in the minimum tooth surface clearance according to the inclination angle when δ = 5 ° as a result of simulation of meshing between the external gear and the internal gear cut by a conventional hobbing machine. The minimum gap takes a minimum value in the vicinity of θ = 90 ° and 270 °, but since the tooth surface is asymmetric with respect to the center of the tooth width, a difference e of about 50 μm occurs between the two minimum values, resulting in misalignment. there is a possibility. This misalignment induces contact between the tooth tip of the external gear and the tooth bottom of the internal gear (contact point S 2 in FIG. 6), and as a result, both gears contact at two locations on the outer circumference that are approximately 90 degrees apart. . Such contact reduces the distance between the fulcrums when the transmission torque is constant. As a result, the contact load becomes larger than when the tooth surfaces are symmetrical, and the surface pressure strength and scoring of the rotating gear coupling are increased. This causes a decrease in strength and an increase in vibration noise.
図9は、基準断面歯形を製品諸元歯数N0よりも多い歯数の対称なインボリュート形状とし、外歯車に成形加工法により対称なクラウニング歯面を与えた本実施例のギヤカップリングにおける回転角と最小隙間の変化を示している。図9に示すように、本実施例のギヤカップリングでは、2箇所の極小値は同じ値となり、ギヤカップリングの外周上の対角の位置で良好な接触が行われる。基準断面歯形が台形の場合も同じである。 FIG. 9 shows a gear coupling according to the present embodiment in which the reference cross-sectional tooth profile is a symmetrical involute shape having a number of teeth greater than the product specification tooth number N 0 and the outer gear is provided with a symmetrical crowning tooth surface by a molding method. The change in the rotation angle and the minimum gap is shown. As shown in FIG. 9, in the gear coupling of the present embodiment, the local minimum values at the two locations are the same value, and good contact is made at diagonal positions on the outer periphery of the gear coupling. The same applies when the reference cross-sectional tooth profile is trapezoidal.
本実施例におけるギヤカップリングの噛み合い状態をシミュレーションした結果を図10〜図12に示す。図10〜図12はハブとスリーブの歯面間隙間を等高線表示した図であって、図10は傾斜角δ=1°(最接近位置)の歯面間隙間を示す図、図11は傾斜角δ=5°(最接近位置)の歯面間隙間を示す図、図12は傾斜角δ=8°(最接近位置)の歯面間隙間を示す図である。なお、図10〜図12においてΔhは等高線ピッチを示している。 The result of having simulated the meshing state of the gear coupling in a present Example is shown in FIGS. 10 to 12 are views showing the gap between the tooth surfaces of the hub and the sleeve in a contour line. FIG. 10 is a view showing the gap between the tooth surfaces at an inclination angle δ = 1 ° (closest position), and FIG. FIG. 12 is a diagram showing a gap between tooth surfaces at an angle δ = 5 ° (closest position), and FIG. 12 is a diagram showing a gap between teeth surfaces at an inclination angle δ = 8 ° (closest position). In FIG. 10 to FIG. 12, Δh indicates a contour line pitch.
本実施例のギヤカップリングの製品諸元歯数N0は40枚、モジュールは3.5であり、基準断面歯形を歯数N=200のインボリュート形状としたものである。また、歯幅は24mm、歯丈2.25×m(m:モジュール)である。なお、図10〜図12において左右方向はハブの歯幅方向を示し、上下方向はハブの歯丈方向であって、下側がハブの歯元側、上側がハブの歯先側を示している。 The product specification tooth number N 0 of the gear coupling of the present embodiment is 40, the module is 3.5, and the reference cross-sectional tooth profile is an involute shape with a tooth number N = 200. The tooth width is 24 mm and the tooth height is 2.25 × m (m: module). 10 to 12, the left-right direction indicates the hub tooth width direction, the up-down direction indicates the hub tooth height direction, the lower side indicates the tooth base side of the hub, and the upper side indicates the tooth tip side of the hub. .
図10〜図12から分かるように、傾斜角がδ=1〜8°と変化しても、歯丈方向における歯の噛み合い位置は変化していない。すなわち、基準断面歯形を製品諸元歯数N0よりも多い歯数のインボリュート形状とすることによって、傾斜角に関係なく歯元から歯先に至るまで、常に良好な歯当たりが得られている。 As can be seen from FIGS. 10 to 12, even if the inclination angle changes from δ = 1 to 8 °, the meshing position of the teeth in the tooth height direction does not change. That is, by setting the reference cross-section tooth profile to an involute shape having a number of teeth greater than the product specification number of teeth N 0 , a good tooth contact is always obtained from the tooth root to the tooth tip regardless of the inclination angle. .
次に、本実施例のギヤカップリングの歯形形状歯数の選定例について説明する。図13から図17はそれぞれギヤカップリングの噛み合い状態をシミュレーションした結果を示している。図13はモジュール3.5,N0=40において基準断面歯形を歯数N=130のインボリュート形状としたもの、図14はモジュール3.5,N0=40において基準断面歯形を歯数N=500のインボリュート形状としたものである。図13および図14に示す例では、歯丈方向における歯の噛み合い位置は変化している。また、歯数Nが増加することによって、接触位置がハブの歯元からハブの歯先に変化する。よって、最適な歯数Nは、中央位置にて噛み合いを行える歯数をシミュレーションによって導出する。 Next, an example of selecting the number of teeth of the gear coupling according to this embodiment will be described. FIG. 13 to FIG. 17 each show the result of simulating the meshing state of the gear coupling. 13 Module 3.5, which the reference sectional tooth profile has an involute shape of the tooth number N = 130 in the N 0 = 40, 14 module 3.5, the number of teeth reference plane tooth in the N 0 = 40 N = 500 involute shapes are used. In the examples shown in FIGS. 13 and 14, the meshing position of the teeth in the tooth height direction is changed. Further, as the number of teeth N increases, the contact position changes from the hub tooth base to the hub tooth tip. Therefore, the optimum number of teeth N is derived by simulation to determine the number of teeth that can be engaged at the center position.
また、図15はモジュール1.5において基準断面歯形を歯数N=700のインボリュート形状としたもの、図16はモジュール2.5において基準断面歯形を歯数N=400のインボリュート形状としたもの、図17はモジュール4.5において基準断面歯形を歯数N=150としたものである。図15〜図17では最適な歯当たりが得られていることが分かる。歯幅、クラウニング量や傾斜角などの設計条件によって最適な歯当たりが得られる歯数は変化するので、これらの設計条件による最適歯数はシミュレーションによって導出する。 15 shows a module 1.5 with an involute shape having a reference cross-sectional tooth profile of N = 700, and FIG. 16 shows a module 2.5 with an involute shape having a reference cross-section tooth profile of N = 400, FIG. 17 shows a module 4.5 in which the reference cross-sectional tooth profile is the number of teeth N = 150. It can be seen from FIGS. 15 to 17 that the optimum tooth contact is obtained. Since the optimum number of teeth can be obtained depending on the design conditions such as tooth width, crowning amount and inclination angle, the optimum number of teeth based on these design conditions is derived by simulation.
図18は実施例と従来例のギヤカップリングにおけるそれぞれの傾斜角δによる噛み合い歯数を示した図である。図18に示すように、実施例のギヤカップリングにおける噛み合い歯数(歯面間隙間が10μm以下となる歯数)は、従来形状と比較して2割程度の増加が認められ、噛み合い歯数が増加することによって、軽量コンパクト化が可能となることが分かった。 FIG. 18 is a diagram showing the number of meshing teeth according to each inclination angle δ in the gear coupling of the example and the conventional example. As shown in FIG. 18, the number of meshing teeth in the gear coupling of the example (the number of teeth where the inter-tooth gap is 10 μm or less) increased by about 20% compared to the conventional shape, and the number of meshing teeth It has been found that an increase in the weight makes it possible to reduce the weight and size.
以上のことから、本実施例のギヤカップリングのように、外歯車および内歯車の基準断面歯形として、外歯車および内歯車の歯数よりも多い歯数のインボリュート歯車の歯形を採用することによって、従来のものより動力伝達能力の向上が見込めることが確認できた。このギヤカップリングでは、傾斜角の変化にかかわらず、噛み合いの接触点の歯形方向の移動量が少なく、片当たりしにくくなるとともに、すべりが少なくなる。その結果、異常摩耗や焼き付きが生じにくく、面圧強度やスコーリング強度(耐焼き付き性能)が向上し、伝達動力が増加する。さらには振動騒音の低下にも繋がる。 From the above, by adopting the tooth profile of the involute gear having a larger number of teeth than the number of teeth of the external gear and the internal gear as the reference cross-sectional tooth profile of the external gear and the internal gear as in the gear coupling of the present embodiment. It was confirmed that the power transmission capacity could be improved compared to the conventional one. In this gear coupling, the amount of movement of the meshing contact point in the tooth profile direction is small regardless of the change in the inclination angle, making it difficult to hit one side and less slipping. As a result, abnormal wear and seizure hardly occur, the surface pressure strength and scoring strength (seizure resistance performance) are improved, and the transmission power is increased. Furthermore, it leads to a reduction in vibration noise.
本発明は、高トルクの動力をコンパクトに伝える用途の中でも特に、大きな傾斜角度を必要とする分野、例えば、鉄道車両の原動機と台車の車軸に組み込まれた歯車装置等の回転軸同士の動力伝達用のギヤカップリングおよびその製造方法として有用である。 The present invention relates to a power transmission between rotating shafts such as a gear device incorporated in a motor vehicle of a railway vehicle and an axle of a bogie, particularly in a field that requires a large inclination angle, among applications for compactly transmitting high torque power. The present invention is useful as a gear coupling for manufacturing and a manufacturing method thereof.
1,11 ギヤカップリング
2a,2b,12a,12b ハブ
3a,3b,13a,13b スリーブ
4a,4b,14a,14b 外歯車
5a,5b,15a,15b 内歯車
1,11 Gear coupling 2a, 2b, 12a, 12b Hub 3a, 3b, 13a, 13b Sleeve 4a, 4b, 14a, 14b External gear 5a, 5b, 15a, 15b Internal gear
Claims (3)
前記外歯車および前記内歯車の基準断面歯形が、前記外歯車および前記内歯車のモジュールと同じモジュールで前記外歯車および前記内歯車の歯数よりも多い歯数のインボリュート歯車の歯形であることを特徴とするギヤカップリング。 In a gear coupling composed of two external gears and an internal gear meshing with the two external gears,
The reference cross-sectional tooth profile of the external gear and the internal gear is a tooth profile of an involute gear having the same number of teeth as the external gear and the internal gear in the same module as the external gear and the internal gear. Features gear coupling.
基準断面歯形を前記外歯車および前記内歯車のモジュールと同じモジュールで前記外歯車および前記内歯車の歯数よりも多い歯数のインボリュート歯車の歯形とする前記外歯車および前記内歯車の歯面を、成形加工法により形成することを特徴とするギヤカップリングの製造方法。 A method for manufacturing a gear coupling comprising two external gears and an internal gear meshing with the two external gears,
A tooth profile of the external gear and the internal gear having a reference cross-sectional tooth profile that is the same as the module of the external gear and the internal gear and having a larger number of teeth than the number of teeth of the external gear and the internal gear. A method for manufacturing a gear coupling, characterized by being formed by a molding method.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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JP2011235262A JP5496982B2 (en) | 2010-12-28 | 2011-10-26 | Gear coupling and manufacturing method thereof |
KR1020110137399A KR101413458B1 (en) | 2010-12-28 | 2011-12-19 | Gear coupling and manufacturing method therefor |
CN201110444241.1A CN102537098B (en) | 2010-12-28 | 2011-12-27 | Toothed coupling and manufacture method thereof |
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JP6730722B2 (en) | 2017-06-29 | 2020-07-29 | 川崎重工業株式会社 | Gear type flexible shaft coupling for railway vehicles and railway vehicle bogie equipped with the same |
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JPS5154040Y2 (en) * | 1972-05-30 | 1976-12-23 | ||
JPS61103720A (en) * | 1984-10-29 | 1986-05-22 | Isuzu Motors Ltd | Control method for cutter of gear finishing machine |
JPS60162737U (en) * | 1985-03-19 | 1985-10-29 | 三菱重工業株式会社 | Anti-vibration joint |
JPH07286623A (en) * | 1994-04-15 | 1995-10-31 | Mitsubishi Electric Corp | Flexible gear joint |
JP2005180631A (en) * | 2003-12-22 | 2005-07-07 | Toyota Motor Corp | Spline component unit and its fitting method |
WO2006137107A1 (en) * | 2005-06-17 | 2006-12-28 | Takamatsu, Toshiro | Hinge unit and door system using the hinge unit |
JP4674140B2 (en) * | 2005-09-16 | 2011-04-20 | ジヤトコ株式会社 | Method for setting optimum number of teeth of helical gear and helical gear |
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JP2010144902A (en) * | 2008-12-22 | 2010-07-01 | Jtekt Corp | Spline fitting structure, sliding type tripod constant velocity joint, and ball-type constant velocity joint |
JP5266140B2 (en) * | 2009-06-01 | 2013-08-21 | 本田技研工業株式会社 | Automatic transmission |
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